Direct manifold boost assist device with throttle body manifold volume isolation

ABSTRACT

Methods and systems are provided for adjusting intake airflow through two induction passages. In response to increased torque demand, intake airflow may be directed through a first induction passage including an exhaust-driven turbocharger compressor and through a second induction passage including an electric compressor. Further, after the turbocharger compressor increases speed, intake airflow may be directed again through the first induction passage to further increase boost.

BACKGROUND/SUMMARY

Turbocharged engines utilize a turbocharger to compress intake air andincrease the power output of the engine. A turbocharger may use anexhaust-driven turbine to drive a compressor which compresses intakeair. As the speed of the compressor increases, increased boost isprovided to the engine. Upon receiving an increased torque demand, itmay take an amount of time for the turbine and compressor to speed upand provide the required boost. This delay in turbocharger response,termed turbo lag, may result in a delay in providing the demanded enginepower. The volume of the induction system of the engine may also delaythe time to pressurize that volume of air. As such, turbo lag andincreased induction system volume may result in engine torque responsedelays.

Other attempts to address turbo lag and engine torque response delaysinclude including an electric assist compressor on the primary inductionpassage. While the electric compressor may provide extra boost, theelectric compressor still has to pressurize the entire induction systemvolume of air, thereby delaying torque response. Another method toreduce engine torque response delays includes utilizing a dualturbocharger arrangement in which two turbochargers are arranged inparallel or in series along the induction path. While the addition of asecond turbocharger may reduce turbo lag, this may also increase thesize and cost of the engine system.

In one example, the issues described above may be addressed by a methodfor controlling intake airflow through two induction flow passages of anengine. A first flow passage may include a turbine-driven compressor anda second flow passage may include an electric compressor. Upon receivingan increased torque request, the electric compressor on the second flowpassage may provide increased boost to an intake manifold of the engine.

In one example, in response to a driver tip-in, a throttle in a firstinduction flow passage, downstream of an exhaust-driven turbochargercompressor, may be temporarily opened. At the same time, an electriccompressor may be driven to also drive flow into an intake manifoldthrough a second induction flow passage, the second flow passage coupledbetween the first induction flow passage, downstream of a charge aircooler, and the intake manifold. Specifically, the throttle may be fullyopened and the electric compressor may be turned on in response to thetip-in, or increased torque demand. Once manifold pressure increases toatmospheric pressure, the throttle may be closed and a compressorrecirculation valve may be opened while continuing driving of theelectric compressor to provide boosted air to the intake manifold.During this time, the turbine-driven compressor may increase speed,thereby increasing boost pressure in the first induction passage. Inresponse to boost pressure increasing above the manifold pressure, thethrottle may open and the compressor recirculation valve may close toprovide the required boost. In this way, turbo lag may be reduced,thereby decreasing the delay in engine torque response.

It should be understood that the summary above is provided to introducein simplified form a selection of concepts that are further described inthe detailed description. It is not meant to identify key or essentialfeatures of the claimed subject matter, the scope of which is defineduniquely by the claims that follow the detailed description.Furthermore, the claimed subject matter is not limited toimplementations that solve any disadvantages noted above or in any partof this disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a schematic diagram of an example engine system including afirst induction flow passage and a first embodiment of a secondinduction flow passage.

FIG. 1B is a schematic diagram of an example engine system including afirst induction flow passage and a second embodiment of a secondinduction flow passage.

FIGS. 2, 3, and 5 are flow charts of methods for adjusting intakeairflow through first and second induction flow passages in response toengine operating conditions.

FIG. 4 is a graphical example of throttle and electric compressoradjustments in response to engine operating conditions.

FIG. 6 is a graphical example of throttle, electric compressor, andcompressor recirculation valve adjustments in response to engineoperating conditions.

DETAILED DESCRIPTION

The following description relates to systems and methods for adjusting aflow of intake air through two induction flow passages. An enginesystem, such as the engine system shown in FIGS. 1A-1B, may include afirst induction flow passage with a turbine-driven compressor and asecond induction flow passage with an electric compressor. In oneexample, as shown in FIG. 1A, the second induction flow passage may beparallel with the first induction flow passage, the second flow passagecoupled between an intake passage, upstream of the turbine-drivencompressor, and an intake manifold. In another example, as shown in FIG.1B, the second induction flow passage may be coupled between the firstinduction flow passage, downstream of a charge air cooler and upstreamof a throttle, and the intake manifold. Flow through the first andsecond induction passages may be controlled by adjusting a position of athrottle in the first induction passage and operation of the electriccompressor. FIGS. 2, 3, and 5 illustrate methods for adjusting thethrottle, compressor recirculation valve, and electric compressor todrive airflow through the first and second induction flow passages inresponse to driving and engine operating conditions. FIGS. 4 and 6 showexample electric compressor and throttle adjustments in response totorque demand, manifold pressure, and boost pressure.

FIG. 1A and FIG. 1B are schematic diagrams showing an example engine 10,which may be included in a propulsion system of an automobile. Theengine 10 is shown with four cylinders or combustion chambers 30.However, other numbers of cylinders may be used in accordance with thecurrent disclosure. Engine 10 may be controlled at least partially by acontrol system including a controller 12, and by input from a vehicleoperator 132 via an input device 130. In this example, the input device130 includes an accelerator pedal and a pedal position sensor 134 forgenerating a proportional pedal position signal PP. Each combustionchamber (e.g., cylinder) 30 of the engine 10 may include combustionchamber walls with a piston (not shown) positioned therein. The pistonsmay be coupled to a crankshaft 40 so that reciprocating motion of thepiston is translated into rotational motion of the crankshaft. Thecrankshaft 40 may be coupled to at least one drive wheel of a vehicleand use engine output torque to propel the automobile. The crankshaft 40may also be used to drive an alternator 152. The alternator 152 may beused to charge and/or power an electric compressor 150. As elaboratedherein, the controller 12 may actuate the operation of the electriccompressor 150. The electric compressor 150 may then be driven usingstored charge or power from the alternator 152.

The combustion chambers 30 may receive intake air from the intakemanifold 44 and may exhaust combustion gases via an exhaust manifold 46to an exhaust passage 48. The intake manifold 44 and the exhaustmanifold 46 can selectively communicate with the combustion chamber 30via respective intake valves and exhaust valves (not shown). In someembodiments, the combustion chamber 30 may include two or more intakevalves and/or two or more exhaust valves.

Fuel injectors 50 are shown coupled directly to the combustion chamber30 for injecting fuel directly therein in proportion to the pulse widthof signal FPW received from controller 12. In this manner, the fuelinjector 50 provides what is known as direct injection of fuel into thecombustion chamber 30; however it will be appreciated that portinjection is also possible. Fuel may be delivered to the fuel injector50 by a fuel system (not shown) including a fuel tank, a fuel pump, anda fuel rail.

In a process referred to as ignition, the injected fuel is ignited byknown ignition means such as spark plug 52, resulting in combustion.Spark ignition timing may be controlled such that the spark occursbefore (advanced) or after (retarded) the manufacturer's specified time.For example, spark timing may be retarded from maximum break torque(MBT) timing to control engine knock or advanced under high humidityconditions. In particular, MBT may be advanced to account for the slowburn rate. In one example, spark may be retarded during a tip-in. Asdiscussed further below, spark timing may also be retarded from MBT toreduce knock when directing warmer intake air through a second inductionflow passage 34 and the intake manifold 44.

The intake manifold 44 may receive intake air from a first inductionflow passage 32 (e.g., first flow passage) and/or a second inductionflow passage 34 (e.g., second flow passage). The intake passage 42 maysupply air to both of these passages. FIG. 1A shows a first embodimentof the second induction flow passage 34 while FIG. 2A shows a secondembodiment of the second induction flow passage 34. These twoembodiments of the second induction flow passage are described furtherbelow.

The first flow passage 32 connects to the intake passage 42 upstream ofan exhaust-driven turbocharger compressor (e.g., compressor) 60. Thefirst flow passage 32 connects to the intake manifold 44 downstream of athrottle 21. Thus, the first flow passage 32 includes the throttle 21having a throttle plate 22 to regulate flow through the first flowpassage 32 and into the intake manifold 44. In this particular example,the position (TP) of the throttle plate 22 may be varied by thecontroller 12 to enable electronic throttle control (ETC). In thismanner, the throttle 21 may be operated to vary the intake air providedfrom the first flow passage 32 to the combustion chambers 30. Forexample, the controller 12 may adjust the throttle plate 22 to increasean opening of the throttle 21. Increasing the opening of the throttle 21may increase the amount of air supplied to the intake manifold 44. In analternate example, the opening of the throttle 21 may be decreased orclosed completely to shut off airflow from the first flow passage 32 tothe intake manifold 44. In some embodiments, additional throttles may bepresent in intake passage 42, such as a throttle upstream of thecompressor 60 (not shown).

Further, in the disclosed embodiments, an exhaust gas recirculation(EGR) system may route a desired portion of exhaust gas from the exhaustpassage 48 to the first flow passage 32 via an EGR passage, such as highpressure EGR passage 140. The amount of EGR provided to the intakepassage 42 may be varied by the controller 12 via an EGR valve, such ashigh pressure EGR valve 142. Under some conditions, the EGR system maybe used to regulate the temperature of the air and fuel mixture withinthe combustion chamber. FIGS. 1A-1B show a high pressure EGR systemwhere EGR is routed from upstream of a turbine of a turbocharger todownstream of a compressor of a turbocharger through EGR passage 140.FIGS. 1A-1B also show a low pressure EGR system where EGR is routed fromdownstream of turbine of a turbocharger to upstream of a compressor of aturbocharger through low pressure EGR passage 156. A low pressure EGRvalve 154 may control the amount of EGR provided to the intake passage42. In some embodiments, the engine may include both a high pressure EGRand a low pressure EGR system, as shown in FIGS. 1A-1B. In otherembodiments, the engine may include either a low pressure EGR system ora high pressure EGR system. When operable, the EGR system may induce theformation of condensate from the compressed air, particularly when thecompressed air is cooled by the charge air cooler, as described in moredetail below.

The engine 10 may further include a compression device such as aturbocharger or supercharger including at least a compressor 60 arrangedalong the first flow passage 32. For a turbocharger, the compressor 60may be at least partially driven by a turbine 62, via, for example ashaft, or other coupling arrangement. The turbine 62 may be arrangedalong the exhaust passage 48. Various arrangements may be provided todrive the compressor. For a supercharger, the compressor 60 may be atleast partially driven by the engine and/or an electric machine, and maynot include a turbine. Thus, the amount of compression provided to oneor more cylinders of the engine via a turbocharger or supercharger maybe varied by the controller 12.

In the embodiment shown in FIGS. 1A-1B, the compressor 60 may be drivenprimarily by the turbine 62. The turbine 62 may be driven by exhaustgases flowing through the exhaust passage 48. Thus, the driving motionof the turbine 62 may drive the compressor 60. As such, the speed of thecompressor 60 may be based on the speed of the turbine 62. As the speedof the compressor 60 increases, more boost may be provided through thefirst flow passage 32 to the intake manifold 44.

Further, the exhaust passage 48 may include a wastegate 26 for divertingexhaust gas away from the turbine 62. Additionally, the intake passage42 may include a compressor bypass or recirculation valve (CRV) 27configured to divert intake air around the compressor 60. The wastegate26 and/or the CRV 27 may be controlled by the controller 12 to be openedwhen a lower boost pressure is desired, for example.

The first flow passage 32 may further include a charge air cooler (CAC)80 (e.g., an intercooler) to decrease the temperature of theturbocharged or supercharged intake gases. In some embodiments, the CAC80 may be an air to air heat exchanger. In other embodiments, the CAC 80may be an air to liquid heat exchanger. The CAC 80 may also be avariable volume CAC. Hot charge air (boosted air) from the compressor 60enters the inlet of the CAC 80, cools as it travels through the CAC, andthen exits to enter the engine intake manifold 44. Ambient air flow fromoutside the vehicle may enter engine 10 through a vehicle front end andpass across the CAC, to aid in cooling the charge air.

Thus, the first flow passage 32 includes the compressor 60, the CAC 80,and the throttle 21. The first flow passage 32 has a first air inductionvolume (e.g., first volume) which includes the air volume of thecompressor 60, the air volume of the CAC 80, and the air volume of theflow path tubing. This air induction volume of the first flow passage 32may delay the time it takes to pressurize the first volume of inductionair. As a result, it may take a duration to supply boosted air to theintake manifold 44. Further, if a large torque demand requires increasedboost, it make take additional time for the compressor to increase to aspeed which produces the required boost. As a result, torque output maybe reduced until the turbocharger speeds up, thereby resulting in turbolag.

In the embodiment shown in FIG. 1A, the second flow passage 34 connectsto the intake passage 42 upstream of the compressor 60 (e.g.,turbine-driven compressor) and connects to the intake manifolddownstream of the throttle 21. As such, the second flow passage 34 isparallel to the first flow passage 32. In an alternate embodiment, asshown in FIG. 1B, the second flow passage 34 is coupled between thefirst flow passage 32, downstream of the CAC 80 and upstream of thethrottle 21, and the intake manifold 44, downstream of the throttle 21.As such, the inlet to the second flow passage 32 is downstream from theCAC 80 and the compressor 60 rather than upstream of the compressor 60,as shown in FIG. 1A. In the embodiment shown in FIG. 1B, cooled chargeair may be pulled into the second flow passage 34 and to the intakemanifold 44. In yet another embodiment, the second flow passage 34 mayinstead connect to the first flow passage 32, upstream of the CAC 80,and then connect to the intake manifold 44 downstream of the throttle21.

The second flow passage 34 includes a boosting element. In theembodiment shown in FIGS. 1A-1B, the boosting element is an electriccompressor 150. In an alternate embodiment, the boosting element may beanother type of driving element such as an air pressure, hydraulic,gear, chain, or belt element driven from the engine. The electriccompressor 150 may be used to boost intake air and supply the boostedair to the intake manifold 44. As described above, the electriccompressor may be powered by stored energy provided by an alternator orother power source. The controller 12 may actuate operation of theelectric compressor 150, including turning the electric compressor on,off, and adjusting a speed of the electric compressor. The speed of theelectric compressor 150 may be based on a torque request. As elaboratedherein, the electric compressor 150 may be operated to control boostedairflow through the second flow passage 34 in response to engineoperating conditions such as boost pressure, intake manifold pressure(MAP), and torque demand.

In one example, the electric compressor 150 may be used to increase ordecrease flow through the second flow passage 34. For example, when theelectric compressor 150 is off (e.g., not spinning), no intake airflowmay enter and flow through the second flow passage 34 to the intakemanifold 44. Thus, air may only flow through the second flow passage 34when the electric compressor 150 is on and being driven by thecontroller 12. As the speed of the electric compressor 150 increases,the amount of airflow and boost delivered to the intake manifold throughthe second flow passage 34 may increase. In some embodiments, the secondflow passage may have an optional throttle 24 having a throttle plate 25to regulate airflow through the second flow passage 34 and into theintake manifold 44. In this particular example, the position of thethrottle plate 25 may be varied by the controller 12. In this manner,the throttle 24 may be operated to vary the amount of intake airprovided from the second flow passage 34 to the intake manifold 44. Forexample, the controller 12 may adjust the throttle plate 25 to increasean opening of the throttle 24. Increasing the opening of the throttle 21may increase the amount of air supplied to the intake manifold 44. In analternate example, the opening of the throttle 24 may be decreased orclosed completely to shut off airflow from the second flow passage 34 tothe intake manifold 44. Alternatively, throttle 24 may be replaced witha one-way valve, allowing a maximum amount of flow into the intakemanifold 44, but not allowing induction air in the first flow passage 32to escape upstream through the second flow passage 34 when the electriccompressor 150 is not being operated.

In alternate embodiments, the second flow passage 34 may include acharge air cooling element, such as a charge air cooler, positioneddownstream from the electric compressor 150. The charge air cooler inthe second flow passage 34 may cool the electrically boosted charge airbefore it enters the intake manifold 44. The charge air cooler may be anair-to-air charge air cooler or a water-to-air charge air cooler.

The second flow passage 34 has a second air induction volume (e.g.,second volume) which includes the air volume of the electric compressor150 and the air volume of the flow path tubing. The second air inductionvolume may be smaller in the embodiment shown in FIG. 1B than theembodiment shown in FIG. 1A. Further, FIGS. 1A-1B may not be drawn toscale. As such, the second flow passage 34 may be shorter than itappears in FIGS. 1A-1B with relation to the first flow passage 32.Additionally, the electric compressor 150 may be positioned proximate tothe intake manifold 44 in order to further reduce the air charge andinduction volume.

The second volume of the second flow passage 34 may be smaller than thefirst volume of the first flow passage 32. As such, the second flowpassage 34 may provide boosted air to the intake manifold 44 morequickly than the first flow passage 32. As described further below withreference to FIGS. 2-3, the controller may adjust the position of thethrottle 21 and operation of the electric compressor 150 to controlairflow through the first and second flow passages. In this way,increased boost may be supplied more quickly in response to an increasedtorque demand, thereby reducing turbo lag.

The controller 12 is shown in FIGS. 1A-1B as a microcomputer, includingmicroprocessor unit 102, input/output ports 104, an electronic storagemedium for executable programs and calibration values shown as read onlymemory chip 106 in this particular example, random access memory 108,keep alive memory 110, and a data bus. The controller 12 may receivevarious signals from sensors coupled to the engine 10 for performingvarious functions to operate the engine 10. In addition to those signalspreviously discussed, these signals may include measurement of inductedmass air flow from MAF sensor 120; engine coolant temperature (ECT) fromtemperature sensor 112, shown schematically in one location within theengine 10; a profile ignition pickup signal (PIP) from Hall effectsensor 118 (or other type) coupled to crankshaft 40; the throttleposition (TP) from a throttle position sensor, as discussed; andabsolute manifold pressure signal, MAP, from sensor 122, as discussed.Engine speed signal, RPM, may be generated by the controller 12 fromsignal PIP. Manifold pressure signal MAP from a manifold pressure sensormay be used to provide an indication of vacuum, or pressure, in theintake manifold 44. Note that various combinations of the above sensorsmay be used, such as a MAF sensor without a MAP sensor, or vice versa.During stoichiometric operation, the MAP sensor can give an indicationof engine torque. Further, this sensor, along with the detected enginespeed, can provide an estimate of charge (including air) inducted intothe cylinder. In one example, the Hall effect sensor 118, which is alsoused as an engine speed sensor, may produce a predetermined number ofequally spaced pulses every revolution of the crankshaft 40.

Other sensors that may send signals to controller 12 include atemperature sensor 124 at an outlet of a charge air cooler 80, and aboost pressure sensor 126. Other sensors not depicted may also bepresent, such as a sensor for determining the intake air velocity at theinlet of the charge air cooler, and other sensors. In some examples,storage medium read-only memory chip 106 may be programmed with computerreadable data representing instructions executable by microprocessorunit 102 for performing the methods described below as well as othervariants that are anticipated but not specifically listed. Exampleroutines are described herein at FIGS. 2-3.

The system of FIG. 1A provides for an engine system including aninduction system with two parallel flow passages to an intake manifoldof the engine. A first flow passage may include a throttle and aturbine-driven compressor. A second flow passage, parallel to the firstflow passage, may include an electric compressor. Specifically, thesecond flow passage may be coupled between an intake passage, upstreamof the turbine-driven compressor, and the intake manifold. The enginesystem may further include a controller with computer readableinstructions for adjusting intake airflow through the first flow passageand the second flow passage in response to driving conditions. In oneexample, driving conditions may include a tip-in and/or torque demandabove or below a threshold.

The system of FIG. 1B provides for an engine system including aninduction system with two flow passages to an intake manifold of theengine. A first flow passage may include a throttle, a charge aircooler, a turbine-driven compressor, and a compressor recirculationvalve operable to direct airflow around the turbine-driven compressor. Asecond flow passage, coupled between the first flow passage, downstreamof the charge air cooler, and the intake manifold, may include anelectric compressor. The engine system may further include a controllerwith computer readable instructions for adjusting intake airflow throughthe first flow passage and the second flow passage in response todriving conditions. In one example, driving conditions may include atip-in and/or torque demand above or below a threshold.

As described above, the intake manifold of the engine may receive intakeair through two induction passages. The first flow path or passage mayinclude an exhaust-driven turbocharger compressor (e.g., driven byturbine) and an intake throttle. The second flow path or passage mayinclude an electric compressor. A controller may adjust a position ofthe intake throttle and operation the electric compressor to adjustairflow through the first and second flow passages. For example, thecontroller may increase an opening of the intake throttle to increase anamount of airflow through the first flow passage. Alternatively, thecontroller may decrease the opening of the intake throttle, increase anopening of the compressor recirculation valve (CRV), and/or actuateoperation of the electric compressor to increase an amount of airflowthrough the second flow passage. In one example, the controller mayclose the throttle and actuate operation of the electric compressor sothat all the intake air travels through the second flow passage. Inanother example, the controller may open the throttle and stop operationof the electric compressor so that all the intake air travels throughthe first flow passage. In yet another example, the controller maypartially open the throttle while operating the electric compressor,thereby allowing intake air to flow through both the first flow passageand the second flow passage.

Additionally, in the embodiment shown in FIG. 1B, the controller mayincrease an opening of the CRV when closing the throttle and directingairflow through the second flow passage. In one example, increasing anopening of the CRV may include fully opening the CRV. In anotherexample, increasing an opening of the CRV may include opening the CRV ifthe CRV is closed. Opening the CRV upon closing the throttle allowsairflow to flow from the intake passage (e.g., intake passage 42 shownin FIG. 1B), through the CRV, into the first flow passage, upstream ofthe second flow passage, and into the second flow passage. While the CRVis open and intake air is traveling through the second flow passage, theturbine may be driving the compressor on the first flow passage. Thecontroller may then decrease the opening of the CRV upon re-opening thethrottle.

The flow of intake air through the first and/or second flow passages maybe controlled in response to engine operating conditions. In oneexample, the electric compressor may normally be off and little to nointake air may flow through the second flow passage. Thus, intake airmay flow through the first flow passage to the intake manifold. Thecontroller may adjust the position of the throttle to increase ordecrease the throttle opening in order to increase or decrease the massair flow to the engine. Additionally, increasing speed of the compressormay increase the boost pressure and MAP of the air entering the intakemanifold of the engine. As such, as turbine and compressor speedincrease, the amount of boost delivered to the intake manifold may alsoincrease. At higher engine torque demand, increased mass air flow andboost may be requested. Thus, the throttle may be controlled in responseto a torque request to supply the required mass air flow for the torquedemand. In some cases, the compressor may not be spinning fast enough toinstantaneously supply the required boost pressure for a given torquerequest. Thus, there may be a delay between when a torque demand isreceived and the requested torque is output by the engine. This delay,referred to herein as turbo lag, may result from the amount of time ittakes the compressor to increase speed and supply the required boost.

In some embodiments, the electric compressor of the second flow passagemay be used to supply boost to the engine. For example, in response totorque demand over a threshold level, the electric compressor may beoperated to supply boosted intake air to the intake manifold. Thethreshold level may be based on the current turbine-driven compressorspeed and the amount of boost required for the torque demand. In oneexample, the threshold level may decrease for a lower compressor speedand higher requested boost level. In another example, the thresholdlevel may be a pre-set level based on the turbocharger. In someexamples, a torque demand over a threshold level may include a tip-in,as indicated by an increase in pedal position and/or throttle position.

The controller may adjust flow through the first and the second flowpassages to supply the requested boost as quickly as possible.Specifically, upon receiving a torque demand greater than a thresholdlevel, the controller may increase the opening of the throttle (e.g.,throttle 21 shown in FIGS. 1A-1B) to direct increased airflow throughthe first flow passage. At the same time, the controller may turn on anddrive the electric compressor to direct intake air through the secondflow passage. The electric compressor may supply boost to the engineintake, thereby allowing torque output to increase. Once the manifoldpressure (e.g., MAP) is at, or greater than, atmospheric pressure, thethrottle may be closed, thereby cutting off airflow through the firstflow passage. The electric compressor may continue to supply boost tothe engine intake. At the same time, the turbine-driven compressor maybe increasing speed as the turbine speed increases. As the compressorspins faster, boost pressure may increase. When boost pressure increasesabove MAP, the controller may re-open the throttle to direct airflowthrough the first flow passage and deliver the required boost for thetorque demand. The throttle (e.g., throttle 21 shown in FIGS. 1A-1B) maybe opened at a controlled rate in order to provide a relatively constantmass air flow transition to the intake manifold. At this time, thecontroller may stop operation of the electric compressor, therebydecreasing airflow through the second flow passage. Directing airflowthrough the two flow passages in this way may decrease the time it takesto deliver boost for an increased torque request, thereby reducing turbolag. Further details on these adjustments are presented below withregard to FIGS. 2-3.

In the embodiment where the second flow passage is coupled between thefirst flow passage, downstream of the CAC, and the intake manifold (asshown in FIG. 1B), the controller may additionally adjust the opening ofthe CRV. For example, when the throttle closes in response to the MAPbeing greater than atmospheric pressure, the controller may also openthe CRV. This allows increased airflow to travel to the second flowpassage and the electric compressor. While the second flow passage issupplying boost to the engine intake, the turbine-driven compressor maybe increasing speed as the turbine speed increases. Little to no loadmay be on the turbine-driven compressor, thereby allowing the speed ofthe turbine-driven compressor to increase at a faster rate. As such, thethrottle may then be re-opened soon than if the CRV remained closedduring this time. When the controller re-opens the throttle in responseto the boost pressure increasing above MAP, the controller may alsoclose the CRV. Further details on these adjustments are presented atFIGS. 2 and 5.

When transitioning from providing intake airflow through the first flowpassage to the second flow passage and the second flow passage to thefirst flow passage, the controller may adjust the throttle and electriccompressor so mass air flow into the intake air flow remains constantand smooth. For example, as discussed above, to transition fromproviding airflow through the first flow passage to providing airflowthrough the second flow passage, the controller may close the throttlein the first flow passage and drive the electric compressor on thesecond flow passage. The closing of the throttle and driving of theelectric compressor may be coordinated so that relatively constant massair flow is provided, at the demanded level, to the intake manifold. Forexample, the controller may turn on the electric compressor instantly,or by slowly increasing the rotation speed while at the same timegradually closing the throttle on the first flow passage. Additionally,the electric compressor may be turned on before, at, or after the pointof closing of the throttle in order to smooth the transition of mass airflow. In this way, the mass air flow level may be maintained at thedemanded level.

Additional engine operating conditions may be adjusted depending onwhich induction flow passage is delivering intake airflow to the intakemanifold. For example, if the throttle is closed and no airflow isflowing through the first flow passage, the high pressure EGR valve maybe closed so no EGR flows into the first flow passage. If the engineincludes a low pressure EGR system, the low pressure EGR valve mayopened to increase EGR flow through the low pressure EGR system whilethe throttle in the first flow passage is closed. Thus, EGR may beprovided from the low pressure EGR system to the second flow passage.

Further, spark timing adjustments may be made based on which inductionflow passage is providing intake airflow and the resulting temperatureof the intake air. For example, the first induction flow passageincludes a CAC to cool compressed air before it enters the intakemanifold. This decreases the temperature of the air entering the enginecylinders, thereby reducing engine knock. However, the second flowpassage may not include a cooling element such as a CAC. Further, asshown in the embodiment in FIG. 1A, the second flow passage may directun-cooled intake air to the intake manifold. Thus, the intake airexiting the second flow passage and entering the intake manifold may bewarmer than the intake air exiting the first flow passage. Warmer intakeair entering the engine cylinders may result in knock. Therefore, underconditions when the second induction flow passage provides intakeairflow to the engine cylinders, spark timing may be retarded to reduceknock. Alternatively, when intake airflow is directed through the firstinduction flow passage, spark timing may be maintained or retarded lessthan when intake airflow is directed through the second induction flowpassage.

As discussed above and shown in FIG. 1B, the inlet to the second flowpassage may be coupled to the first flow passage, downstream from theCAC. In this embodiment, spark timing may be retarded less or maintainedsince the charge air may already be partially cooled. In alternateembodiments, the second flow passage may also include a charge aircooler or other means of cooling the charge air after passing throughthe electric compressor. In this example, spark timing adjustments maynot be necessary. Thus, spark timing adjustments may depend on theconfiguration of the second flow passage and subsequently the amount ofcooling provided to the charge air.

Retarding spark timing may result in an amount of torque loss. As sparkis retarded further, the amount of torque loss may increase. Thus,directing airflow through the second flow passage may result in torqueloss due to retarding spark to avoid knock. However, directing airflowthrough the first flow passage may also result in torque loss due toturbo lag. For example, torque loss may result from the amount of timeit takes the turbine-driven compressor to speed up to deliver therequired boost. In some cases, the torque loss from retarding spark maybe greater than the torque loss from turbo lag. Under these conditions,airflow may be directed through the first flow passage instead of thesecond flow passage, even if torque demand is greater than the thresholdlevel. Methods for adjusting intake airflow through the first and secondflow passages based on torque loss is discussed further below withreference to FIGS. 2-3 and 5.

In this way, in response to a driver tip-in, a throttle in a firstinduction flow passage, downstream of an exhaust-driven turbochargercompressor, may be temporarily opened. In one example, the driver tip-inmay be indicated by an increase in pedal position. Additionally, inresponse to the driver tip-in, an electric compressor may beelectrically driven to drive flow into an intake manifold through asecond induction flow passage. In one example, the second induction flowpassage may be in parallel with the first induction flow passage. Inanother example, the second induction flow passage may be coupledbetween the first induction flow passage, downstream of a charge aircooler, and the intake manifold.

In one example, temporarily opening the throttle includes opening thethrottle to a threshold opening and maintaining the threshold opening toincrease a manifold pressure from below a threshold pressure to thethreshold pressure. A controller may then close the throttle in responseto the manifold pressure increasing to the threshold pressure. In oneexample, the controller additionally opens a compressor recirculationvalve in response to the manifold pressure increasing to the thresholdpressure. The threshold pressure may be atmospheric pressure.

Electrically driving the electric compressor includes driving theelectric compressor at a speed based on a required boost level for atorque demand during the tip-in. The throttle may be re-opened inresponse to a boost pressure being greater than a manifold pressure.Upon re-opening the throttle, the controller may stop electricallydriving the electric compressor. In one embodiment, the controller mayadditionally close the compressor recirculation valve upon re-opening ofthe throttle. In another example, re-opening the throttle may beresponsive to a power level of the electric compressor decreasing belowa threshold level. Further, spark retard may be increased during thedriving the electric compressor to drive flow into the intake manifoldthrough the second induction flow passage.

FIG. 2 shows a method 200 for determining which induction flow passageto direct intake air through and to the intake manifold. The methodbegins at 202 by estimating and/or measuring engine operatingconditions. Engine operating conditions may include engine speed andload, pedal position (PP), torque demand, spark timing, throttleposition, MAP, boost pressure, mass air flow, etc. At 204, the methodincludes determining if torque demand is greater than a threshold level.In one example, an increase in torque demand may be indicated by anincrease in throttle position and/or pedal position. In another example,a torque demand greater than a threshold level may result from a drivertip-in. The driver tip-in may be indicated by a sudden increase in pedalposition. Further, the threshold level may be based on a torque demandthat may result in turbo lag. For example, it may take a duration forthe turbine-driven compressor to produce the required boost for thethreshold level of torque demand. This duration may result in a delay intorque output of the engine. As such, the threshold level may be furtherbased on a current compressor speed and/or boost pressure.

Returning to 204, if the torque demand is not greater than thethreshold, the controller may direct intake air through the first flowpassage at 206. Directing airflow through the first flow passage mayinclude adjusting throttle position based on the torque demand. Further,the controller may maintain the electric compressor off at 206 so mostor all of the intake air travels through the first flow passage. In oneexample, the second flow passage may include a throttle or one-way valvewhich is closed to block air from flowing through the second flowpassage. Alternatively, if torque demand is greater than a threshold at204, the method continues on to 208 to increase the opening of thethrottle (e.g., the throttle in the first flow passage). In one example,this may include opening the throttle to a threshold opening. Thethreshold opening may be a maximal amount of opening such that thethrottle is fully opened. Increasing the opening of the throttle at 208may result in an increase in mass air flow and MAP.

At 212, the controller directs intake air through the second flowpassage if secondary flow path conditions are met. As described furtherat FIG. 3, these conditions may include a torque loss from spark retardbeing less than a torque loss from turbo lag. In a first example, aspresented further at FIG. 3, directing intake air through the secondflow passage may include closing the intake throttle on the first flowpassage and driving the electric compressor. In a second example, aspresented further at FIG. 5, directing intake air through the secondflow passage may include closing the intake throttle and opening the CRVon the first flow passage and driving the electric compressor.

FIG. 3 shows a method 300 for adjusting intake airflow through the firstand second flow passages (such as the first and second flow passages 32and 34, respectively, shown in FIG. 1A) in response to engine operatingconditions. Specifically, method 300 continues on from method 200 todirect airflow through a first embodiment of the second flow passage, asshown in FIG. 1A. In this embodiment, directing airflow through thesecond flow passage includes flowing intake air from upstream of theturbine-driven compressor, through the second flow passage, and to theintake manifold.

Airflow may be directed through the second flow passage when torquedemand increases above a threshold level (as described at 204 in method200) and the secondary flow path conditions are met. As described above,the secondary flow path conditions may include when an expected torqueloss from spark retard is less than an expected torque loss from turbolag. As such, at 301 the method includes determining if the torque lossfrom spark retard is less than the torque loss from turbo lag. Thetorque loss from spark retard may be the resulting torque loss due toretarding spark to reduce knock while directing warmer air through thesecond flow passage. The torque loss from turbo lag may be the resultingtorque loss due to directing airflow through the first flow passage andwaiting for the turbine-driven compressor to produce the required boostfor the torque demand. If the torque loss from retarding spark is notless than the torque loss due to turbo lag (e.g., torque loss from sparkretard is greater than torque loss from turbo lag), the method continueson to 302 to direct airflow through the first flow passage. Thus, eventhough torque demand is greater than the threshold, intake airflow isdirected through the first flow passage to reduce losses in enginetorque output. However, if at 301 the torque loss from spark retard isless than the torque loss from turbo lag, the controller directs intakeair through the second flow passage at 303. Thus, in some examples, thecontroller may simultaneously open the intake throttle in the first flowpassage (as described and direct airflow through the second flow passageto increase boost.

Specifically, at 303, the controller drives the electric compressor anddirects intake air through the second flow passage. Driving thecompressor at 302 may include turning on the electric compressor andoperating the electric compressor at a speed based on a required boostlevel for the torque demand. For example, the electric compressor mayremain off until torque demand and/or pedal position increases above athreshold. At that point, the speed of the electric compressor mayincrease with increasing torque demand. In another example, the electriccompressor may only turn on or off. As such, the electric compressor mayonly operate at one speed when turned on. In yet another example, theoperation speed of the electric compressor may be based on an amount ofpower stored (e.g., power available) at the electric compressor. Forexample, if less power is available for electric compressor operation,the electric compressor may be driven at a lower speed than required bythe boost level.

After turning on the electric compressor, the controller may adjustspark timing at 304. Spark timing adjustments may be based on atemperature of the charge air traveling through the second flow passageand entering the intake manifold of the engine. For example, in responseto driving the electric compressor to direct warmer intake air throughthe second flow passage, the controller may retard spark timing at 304.The amount of spark retard may be based on the temperature of the airtraveling through the second flow passage and/or the driving speed ofthe electric compressor. For example, for a larger torque demand, theelectric compressor may spin at a faster rate to provide increasedboost. This may increase the temperature of the intake air entering theengine cylinders, thereby increasing the risk of knock. As a result,spark may be retarded by a larger amount. The controller may continue toadjust spark during the directing intake air through the second flowpassage. For example, after closing the throttle (described furtherbelow at 312), the controller may increase the amount of spark retarddue to an increased amount of warmer air traveling to the intakemanifold.

At 308, the method includes determining if MAP is at or above athreshold pressure. In one example, the threshold pressure isatmospheric pressure. In another example, the threshold pressure may bea pressure greater or less than atmospheric pressure. If MAP is stillbelow the threshold pressure at 308, the controller maintains thecurrent throttle opening at 310. Once MAP reaches and/or increases abovethe threshold pressure, the controller closes the throttle on the firstflow passage at 312. Closing the throttle at 312 may include slowlydecreasing the opening of the throttle to provide relatively smooth massair flow to the engine intake. In this way, continuous mass air flow maybe provided to the intake manifold.

During the driving the electric compressor, the turbine-drivencompressor may be increasing speed. As a result, the boost pressure,downstream of the turbine-driven compressor, may increase. At 314, themethod determines if the boost pressure is greater than MAP. If boostpressure is not greater than MAP, the controller continues driving theelectric compressor and maintains the throttle closed at 316. However,if the boost pressure is greater than MAP, the method continues on to318 to open the throttle to deliver the required boost for the torquedemand. Upon opening the throttle, the controller stops driving theelectric compressor at 320. This may include stopping airflow throughthe second flow passage. Further, the method at 320 may includereturning spark timing to its original or currently requested level. Insome embodiments, the steps at 318 and 320 may occur concurrently toprovide smooth and continuous mass air flow. In one example, this mayinclude increasing the opening of the throttle while slowing down andeventually stopping the compressor.

Alternatively, if the electric compressor runs out of power before theboost pressure increase above MAP, the throttle may be opened anyway.For example, method 300 may have an extra step after 314 and before 316which checks the power level of the electric compressor. If the powerlevel of the electric compressor is below a threshold level, the methodmay continue on to 318 to re-open the throttle, even if boost pressureis not greater than MAP. The electric compressor would then be turnedoff at 320 so that it may re-charge for subsequent tip-ins.

In this way, a controller may adjust intake airflow through a first flowpassage and a second flow passage in response to driving conditions. Inone example, adjusting intake airflow includes increasing an opening ofthe throttle to direct airflow through the first flow passage responsiveto a torque demand less than a threshold. In another example, adjustingintake airflow includes initially increasing an opening of the throttleand driving the electric compressor to simultaneously direct airflowthrough the first flow passage and the second flow passage responsive toa torque demand greater than a threshold. The throttle may then beclosed after the initial increase in opening responsive to a manifoldpressure greater than atmospheric pressure. Adjusting intake airflow mayfurther include increasing an opening of the throttle and stoppingdriving the electric compressor to direct airflow through the first flowpassage responsive to a torque demand greater than a threshold and aboost pressure greater than a manifold pressure.

FIG. 5 shows a method 500 for adjusting intake airflow through the firstand second flow passages (such as the first and second flow passages 32and 34, respectively, shown in FIG. 1B) in response to engine operatingconditions. Specifically, method 500 continues on from method 200 todirect airflow through a second embodiment of the second flow passage,as shown in FIG. 1B. In this embodiment, directing airflow through thesecond flow passage includes flowing intake air from downstream of acharge air cooler on the first flow passage, through the second flowpassage, and to the intake manifold.

Airflow may be directed through the second flow passage when torquedemand increases above a threshold level (as described at 204 in method200). Thus, after increasing the opening of the throttle (as describedat 208 in method 200), the controller may drive the electric compressorand direct intake air through the second flow passage at 502. Asdiscussed above, driving the compressor at 502 may include turning onthe electric compressor and operating the electric compressor at a speedbased on a required boost level for the torque demand. For example, theelectric compressor may remain off until torque demand and/or pedalposition increases above a threshold. At that point, the speed of theelectric compressor may increase with increasing torque demand. Inanother example, the electric compressor may only turn on or off. Assuch, the electric compressor may only operate at one speed when turnedon. In yet another example, the operation speed of the electriccompressor may be based on an amount of power stored (e.g., poweravailable) at the electric compressor. For example, if less power isavailable for electric compressor operation, the electric compressor maybe driven at a lower speed than required by the boost level.

After turning on the electric compressor, the controller may adjustspark timing at 504. Spark timing adjustments may be based on atemperature of the charge air traveling through the second flow passageand entering the intake manifold of the engine. Since the second flowpassage is coupled between the first flow passage, after the CAC, andthe intake manifold in this embodiment, less spark retard may benecessary. For example, the air traveling through the second flowpassage may be partially cooled (e.g., cooled by the CAC in the firstflow passage). In some embodiments, if the second flow passage includesa charge air cooling element, little to no spark adjustments may benecessary at 504.

At 508, the method includes determining if MAP is at or above athreshold pressure. In one example, the threshold pressure isatmospheric pressure. In another example, the threshold pressure may bea pressure greater or less than atmospheric pressure. If MAP is stillbelow the threshold pressure at 508, the controller maintains thecurrent throttle opening at 510. Once MAP reaches and/or increases abovethe threshold pressure, the controller closes the throttle on the firstflow passage and opens the CRV at 512. Closing the throttle and openingthe CRV at 512 may include slowly decreasing the opening of the throttleand increasing the opening of the CRV to provide relatively smooth massair flow to the engine intake. In this way, continuous mass air flow maybe provided to the intake manifold.

During the driving the electric compressor, the turbine-drivencompressor may be increasing speed. As a result, the boost pressure,downstream of the turbine-driven compressor, may increase. At 514, themethod determines if the boost pressure is greater than MAP. If boostpressure is not greater than MAP, the controller continues driving theelectric compressor and maintains the throttle closed at 516. However,if the boost pressure is greater than MAP, the method continues on to518 to open the throttle to deliver the required boost for the torquedemand. Upon opening the throttle, the controller stops driving theelectric compressor and closes the CRV at 520. This may include stoppingairflow through the second flow passage. Further, the method at 520 mayinclude returning spark timing to its original or currently requestedlevel. In some embodiments, the steps at 518 and 520 may occurconcurrently to provide smooth and continuous mass air flow. In oneexample, this may include increasing the opening of the throttle whileslowing down and eventually stopping the compressor.

Alternatively, if the electric compressor runs out of power before theboost pressure increase above MAP, the throttle may be opened anyway.For example, method 500 may have an extra step after 514 and before 516which checks the power level of the electric compressor. If the powerlevel of the electric compressor is below a threshold level, the methodmay continue on to 518 to re-open the throttle, even if boost pressureis not greater than MAP. The electric compressor would then be turnedoff at 520 so that it may re-charge for subsequent tip-ins.

In this way, a controller may adjust intake airflow through a first flowpassage and a second flow passage in response to driving conditions. Inone example, adjusting intake airflow includes increasing an opening ofthe throttle to direct airflow through the first flow passage responsiveto a torque demand less than a threshold. In another example, adjustingintake airflow includes initially increasing an opening of the throttleand driving the electric compressor to simultaneously direct airflowthrough the first flow passage and the second flow passage responsive toa torque demand greater than a threshold. Then, the throttle may beclosed and the compressor recirculation valve may be opened after theinitial increase in opening responsive to a manifold pressure greaterthan atmospheric pressure. Adjusting intake airflow may further includeincreasing an opening of the throttle, closing the compressorrecirculation valve, and stopping driving the electric compressor todirect airflow through the first flow passage responsive to a torquedemand greater than a threshold and a boost pressure greater than amanifold pressure.

FIG. 4 illustrates a graphical example of throttle and electriccompressor adjustments in response to engine operating conditions. Theadjustments in FIG. 4 are for a first embodiment of a second flowpassage as illustrated in FIG. 1A. Specifically, graph 400 shows changesin pedal position at plot 402, changes in torque demand at plot 404,changes in throttle position (TP) at plot 406, changes in MAP (e.g.,manifold pressure) at plot 408, changes in boost pressure at plot 410,changes in electric compressor operation at plot 412, and changes inspark timing at plot 418. A tip-in may be indicated at plot 402 by asudden increase in pedal position. The throttle position may be betweena closed and fully open position, as shown at plot 406. In one example,base operation of the electric compressor may be off. Operation of theelectric compressor and increases in electric compressor speed areindicated at plot 412. Finally, spark timing may be retarded or advancedfrom MBT, as shown at plot 418.

Before time t1, pedal position is at a steady position (plot 402),torque demand is below the threshold level 414 (plot 404), and sparktiming is near MBT (plot 418). Further, the throttle is partially open(406), MAP and boost pressure are below the threshold pressure 416(e.g., atmospheric pressure), and the electric compressor is off. Assuch, intake airflow may be traveling through the first flow passage andnot through the second flow passage.

At time t1, pedal position increases gradually (plot 402). This causestorque demand to increase; however, it remains below the threshold level414 (plot 404). As a result, throttle position increases (plot 406),thereby increasing mass air flow to the intake manifold. Boost pressureincreases, increasing MAP above the threshold pressure 416 (plots 408and 410). The electric compressor remains off since torque demand isless than the threshold level 414. Spark timing may retard slightly fromMBT in response to the increase in pedal position. At time t2, pedalposition decreases (plot 402) and returns to a steady, lower level. Inresponse, torque demand and throttle position decrease, therebydecreasing MAP and boost pressure.

At time t3, a tip-in occurs, as indicated by a sudden increase in pedalposition (plot 402), thereby increasing torque demand above thethreshold level 414. In response to the tip-in, the controller increasesthe throttle opening so that it is fully opened (plot 406) and turns onthe electric compressor. As such, charge air may be supplied to theintake manifold through both the first flow passage and the second flowpassage from time t3 to time t4. MAP and boost pressure increase and attime t4, MAP reaches the threshold pressure 416. As a result, thethrottle opening is decreased and eventually closed, cutting off airflowthrough the first flow passage. The controller continues to drive theelectric compressor to provide boost to the intake manifold.Additionally, the controller may further retard spark at time t4 andcontinue retarding spark while the electric compressor is on and drivingairflow through the second flow passage. Between time t4 and time t5,MAP continues to increase as intake air travels through the electriccompressor and to the intake manifold. Meanwhile, as the turbine-drivencompressor speeds up and continues to run, boost pressure increases(plot 410). At time t5, boost pressure increases above MAP. As a result,the controller increases the opening of the throttle to deliver therequested boot for the torque demand. The controller also stops drivingthe compressor, turning the compressor off and cutting off airflowthrough the second flow passage (plot 412). At time t6, the tip-in ends,decreasing torque demand and the throttle opening.

At time t7, another tip-in occurs (plot 402). Torque demand increasesabove the threshold level 414. However, the torque loss due to retardingspark when directing airflow through the second flow passage may begreater than the torque loss due to turbo lag when directing airflowthrough the first flow passage. Thus, even though torque demand isgreater than the threshold level 414, the controller opens the throttleto direct airflow through the first flow passage (plot 406) andmaintains the electric compressor off (plot 412). At time t8, the tip-inends and the throttle opening is returned to the currently demandedlevel.

As shown in graph 400, intake airflow may be directed through first andsecond parallel flow passages. In one example, during a first condition(as shown at times t1 and t7), intake airflow is directed through thefirst flow passage including a throttle and a turbine-driven compressor.Directing intake airflow through the first flow passage includesincreasing an opening of the throttle. In a first example, as shown attime t1, the first condition includes when a torque demand is less thana threshold. In a second example, as shown at time t7, the firstcondition includes when the torque demand is greater than the thresholdand a torque loss from retarding spark due to directing intake airflowthrough the second flow passage is greater than a torque loss from turbolag.

In another example, during a second condition (as shown at time t4),intake airflow is directed through a second flow passage including anelectric compressor, the second flow passage parallel to the first flowpassage. Directing intake airflow through the second flow passageincludes driving the electric compressor and closing the throttle when amanifold pressure is at or greater than a threshold pressure. As shownat time t4, the second condition includes when a torque demand ingreater than a threshold and a torque loss from retarding spark duringthe directing intake airflow through the second flow passage is lessthan a torque loss from turbo lag.

During a third condition, as shown at time t5, when a boost pressure isgreater than the manifold pressure during driving intake airflow throughthe second flow passage, the throttle is opened to direct intake airflowthrough the first flow passage. Further, during the third condition, thecontroller stops driving the electric compressor to stop airflow fromflowing through the second flow passage.

FIG. 6 illustrates a graphical example of throttle, compressorrecirculation valve (CRV), and electric compressor adjustments inresponse to engine operating conditions. The adjustments in FIG. 6 arefor a second embodiment of a second flow passage as illustrated in FIG.1B. Specifically, graph 600 shows changes in pedal position at plot 602,changes in torque demand at plot 604, changes in throttle position (TP)at plot 606, changes in MAP (e.g., manifold pressure) at plot 608,changes in boost pressure at plot 610, changes in electric compressoroperation at plot 612, changes in spark timing at plot 618, and changesin CRV position at plot 620. A tip-in may be indicated at plot 602 by asudden increase in pedal position. The throttle position may be betweena closed and fully open position, as shown at plot 606. In one example,base operation of the electric compressor may be off. Operation of theelectric compressor and increases in electric compressor speed areindicated at plot 612. Additionally, the CRV position may be between aclosed and fully open position, as shown at plot 620. However, inalternate examples, the position of the CRV may be between closed andfully opened. Finally, spark timing may be retarded or advanced fromMBT, as shown at plot 618.

Before time t1, pedal position is at a steady position (plot 602),torque demand is below the threshold level 614 (plot 604), and sparktiming is near MBT (plot 618). Further, the throttle is partially open(plot 606), MAP and boost pressure are below the threshold pressure 616(e.g., atmospheric pressure), the electric compressor is off (plot 612),and the CRV is closed (plot 620). As such, intake airflow may betraveling through the first flow passage and not through the second flowpassage.

At time t1, pedal position increases gradually (plot 602). This causestorque demand to increase; however, it remains below the threshold level614 (plot 604). As a result, throttle position increases (plot 606),thereby increasing mass air flow to the intake manifold. Boost pressureincreases, increasing MAP above the threshold pressure 616 (plots 608and 610). The electric compressor remains off and the CRV remains closedsince torque demand is less than the threshold level 614. Spark timingmay retard slightly from MBT in response to the increase in pedalposition. At time t2, pedal position decreases (plot 602) and returns toa steady, lower level. In response, torque demand and throttle positiondecrease, thereby decreasing MAP and boost pressure.

At time t3, a tip-in occurs, as indicated by a sudden increase in pedalposition (plot 602), thereby increasing torque demand above thethreshold level 614. In response to the tip-in, the controller increasesthe throttle opening so that it is fully opened (plot 606) and turns onthe electric compressor. As such, charge air may be supplied to theintake manifold through both the first flow passage and the second flowpassage from time t3 to time t4. MAP and boost pressure increase and attime t4, MAP reaches the threshold pressure 616. As a result, thethrottle opening is decreased and eventually closed, cutting off airflowthrough the first flow passage. At this time, the controller opens theCRV (plot 620). In alternate embodiments, opening the CRV at time t4 mayinclude partially opening the CRV. The controller continues to drive theelectric compressor to provide boost to the intake manifold.Additionally, the controller may further retard spark at time t4 andcontinue retarding spark while the electric compressor is on and drivingairflow through the second flow passage. However, less spark retard maybe required in this second embodiment of the second flow passage than inthe first embodiment of the second flow passage, as shown in FIG. 4.Between time t4 and time t5, MAP continues to increase as intake airtravels through the electric compressor and to the intake manifold.Meanwhile, as the turbine-driven compressor speeds up and continues torun, boost pressure increases (plot 610). At time t5, boost pressureincreases above MAP. As a result, the controller closes the CRV andincreases the opening of the throttle to deliver the requested boot forthe torque demand. The controller also stops driving the compressor,turning the compressor off and cutting off airflow through the secondflow passage (plot 612). At time t6, the tip-in ends, decreasing torquedemand and the throttle opening.

As shown in graph 600, intake airflow may be directed through first andsecond flow passages. In one example, during a first condition (as shownat time t1), intake airflow is directed through the first flow passageincluding a throttle and a turbine-driven compressor. Directing intakeairflow through the first flow passage includes increasing an opening ofthe throttle. As shown at time t1, the first condition includes when atorque demand is less than a threshold.

In another example, during a second condition (as shown at time t4),intake airflow is directed through a second flow passage including anelectric compressor, the second flow passage coupled between the firstflow passage, downstream of a charge air cooler, and an intake manifold.Directing intake airflow through the second flow passage includesdriving the electric compressor and closing the throttle and opening acompressor recirculation valve when a manifold pressure is at or greaterthan a threshold pressure. As shown at time t4, the second conditionincludes when a torque demand in greater than a threshold.

During a third condition, as shown at time t5, when a boost pressure isgreater than the manifold pressure during driving intake airflow throughthe second flow passage, the throttle is opened to direct intake airflowthrough the first flow passage. Further, during the third condition, thecontroller stops driving the electric compressor to stop airflow fromflowing through the second flow passage and closes the compressorrecirculation valve.

In this way, in response to a torque demand and engine operatingconditions, required boost for the torque demand may be provided byadjusting airflow through first and second induction flow passages. Thefirst flow passage may include a throttle and a turbine drivencompressor. In one example, in response to a tip-in, a controller maysimultaneously direct intake airflow through the first flow passage andthe second flow passage by increasing the opening the throttlepositioned in the first flow passage and driving an electric compressorpositioned in the second flow passage. When a manifold pressure reachesatmospheric pressure, the controller may close the throttle and continuedriving the electric compressor. In some embodiments, the controller mayadditionally open a compressor recirculation valve. The electriccompressor may provide the required boost to the intake manifold while aboost pressure downstream of the turbine-driven compressor increases.When the boost pressure in the second flow passage increases above themanifold pressure, the controller may re-open the throttle to provideadditional boost and stop driving the compressor. In this way, turbo lagmay be reduced and required boost for the torque demand may be providedto the engine.

An embodiment relates to an engine system comprising an induction systemwith two parallel flow passages to an intake manifold of the engine, afirst flow passage including a throttle and a turbine-driven compressor,a second flow passage, parallel to the first flow passage, including anelectric compressor, and a controller with computer readableinstructions for adjusting intake airflow through the first flow passageand the second flow passage in response to driving conditions. In oneexample, adjusting intake airflow includes increasing an opening of thethrottle to direct airflow through the first flow passage responsive toa torque demand less than a threshold. In another example, adjustingintake airflow includes initially increasing an opening of the throttleto direct airflow through the first flow passage and driving theelectric compressor to direct airflow through the second flow passageresponsive to a torque demand greater than a threshold and closing thethrottle after the initial increase in opening responsive to a manifoldpressure greater than atmospheric pressure. Adjusting intake airflowfurther includes increasing an opening of the throttle to direct airflowthrough the first flow passage responsive to a torque demand greaterthan a threshold and a boost pressure greater than a manifold pressure.

Another embodiment relates to an engine system comprising an inductionsystem with two flow passages to an intake manifold of the engine; afirst flow passage including a throttle, a charge air cooler, aturbine-driven compressor, and a compressor recirculation valve operableto direct airflow around the turbine-driven compressor; a second flowpassage, coupled between the first flow passage, downstream of thecharge air cooler, and the intake manifold, including an electriccompressor; and a controller with computer readable instructions foradjusting intake airflow through the first flow passage and the secondflow passage in response to driving conditions. In one example,adjusting intake airflow includes increasing an opening of the throttleto direct airflow through the first flow passage responsive to a torquedemand less than a threshold. In another example, adjusting intakeairflow includes initially increasing an opening of the throttle todirect airflow through the first flow passage and driving the electriccompressor to direct airflow through the second flow passage responsiveto a torque demand greater than a threshold and closing the throttle andopening the compressor recirculation valve after the initial increase inopening responsive to a manifold pressure greater than atmosphericpressure. Adjusting intake airflow further includes increasing anopening of the throttle to direct airflow through the first flow passageresponsive to a torque demand greater than a threshold and a boostpressure greater than a manifold pressure.

A further embodiment relates to an engine method comprising directingintake airflow through a flow passage including a turbine-drivencompressor followed by a charge air cooler with a compressor bypassvalve opened, while compressing air cooled by the charge air cooler byan electrically-driven compressor and directing it to an intakemanifold. The directing is in response to a driver tip-in, and thecompressing by the electrically-driven compressor is reduced whileclosing the compressor bypass valve after the turbine-driven compressoris spun up to a threshold level. Further, the air compressed by theelectrically-driven compressor is delivered to the intake manifold whilebypassing a throttle in a parallel passage. Additionally, an exhaust gasrecirculation valve is fully closed while directing intake airflowthrough the flow passage and compressing air cooled by the charge aircooler.

Note that the example control routines included herein can be used withvarious engine and/or vehicle system configurations. The specificroutines described herein may represent one or more of any number ofprocessing strategies such as event-driven, interrupt-driven,multi-tasking, multi-threading, and the like. As such, various acts,operations, or functions illustrated may be performed in the sequenceillustrated, in parallel, or in some cases omitted. Likewise, the orderof processing is not necessarily required to achieve the features andadvantages of the example embodiments described herein, but is providedfor ease of illustration and description. One or more of the illustratedacts or functions may be repeatedly performed depending on theparticular strategy being used. Further, the described acts maygraphically represent code to be programmed into the computer readablestorage medium in the engine control system.

It will be appreciated that the configurations and routines disclosedherein are exemplary in nature, and that these specific embodiments arenot to be considered in a limiting sense, because numerous variationsare possible. For example, the above technology can be applied to V-6,I-4, I-6, V-12, opposed 4, and other engine types. Further, one or moreof the various system configurations may be used in combination with oneor more of the described diagnostic routines. The subject matter of thepresent disclosure includes all novel and non-obvious combinations andsub-combinations of the various systems and configurations, and otherfeatures, functions, and/or properties disclosed herein.

The invention claimed is:
 1. An engine method, comprising: in responseto a driver tip-in, temporarily opening a throttle in a first inductionflow passage, downstream of an exhaust-driven turbocharger compressor,and electrically driving an electric compressor to drive flow into anintake manifold through a second induction flow passage, the secondinduction flow passage coupled between the first induction flow passage,downstream of a charge air cooler, and the intake manifold; and inresponse to a pressure of the intake manifold increasing to a thresholdpressure during the driving the electric compressor, closing thethrottle and opening a compressor recirculation valve configured todivert intake air around the turbocharger compressor.
 2. The method ofclaim 1, wherein temporarily opening the throttle includes opening thethrottle to a threshold opening and maintaining the threshold opening toincrease a manifold pressure from below the threshold pressure to thethreshold pressure.
 3. The method of claim 1, wherein closing thethrottle and opening the compressor recirculation valve includes slowlydecreasing the opening of the throttle while slowly increasing theopening of the compressor recirculation valve to provide relativelysmooth mass air flow to the intake manifold.
 4. The method of claim 1,wherein the threshold pressure is atmospheric pressure.
 5. The method ofclaim 1, wherein electrically driving the electric compressor includesdriving the electric compressor at a speed based on a required boostlevel for a torque demand during the tip-in.
 6. The method of claim 1,further comprising re-opening the throttle in response to a boostpressure being greater than the pressure of the intake manifold.
 7. Themethod of claim 6, further comprising, upon re-opening the throttle,stopping electrically driving the electric compressor and closing thecompressor recirculation valve.
 8. The method of claim 6, wherein there-opening the throttle is further responsive to a power level of theelectric compressor decreasing below a threshold level, even if boostpressure is not greater than the pressure of the intake manifold.
 9. Themethod of claim 1, wherein the driver tip-in is indicated by an increasein pedal position and further comprising, in response to a torque demandbeing less than a threshold torque demand, directing intake air throughthe first induction flow passage, maintaining the electric compressoroff, and adjusting the throttle based on the torque demand to supply arequired mass air flow for the torque demand.
 10. The method of claim 1,further comprising adjusting spark timing during the driving theelectric compressor based on a temperature at the intake manifold. 11.An engine method, comprising: during a first condition, directing intakeairflow through a first flow passage including a first throttle and aturbine-driven compressor and adjusting the first throttle to deliver ademanded torque; during a second condition, directing intake airflowthrough a second flow passage including an electric compressor, thesecond flow passage coupled between the first flow passage, downstreamof a charge air cooler, and an intake manifold; and during the secondcondition, in response to a pressure of the intake manifold reaching orincreasing above a threshold pressure, closing the first throttle andopening a compressor recirculation valve disposed in a passage aroundthe turbine-driven compressor.
 12. The method of claim 11, wherein thedemanded torque is a driver demanded torque and wherein directing intakeairflow through the first flow passage includes increasing an opening ofthe first throttle in response to the driver demanded torque to supply arequired mass air flow for the driver demanded torque.
 13. The method ofclaim 11, wherein the first condition includes when a torque demand isat or less than a threshold and the second condition includes when thetorque demand is greater than the threshold.
 14. The method of claim 11,wherein directing intake airflow through the second flow passageincludes driving the electric compressor, wherein the second flowpassage includes a second throttle, and further comprising adjusting thesecond throttle to vary an amount of intake air provided to the intakemanifold from the second flow passage.
 15. The method of claim 11,wherein the first condition includes when torque demand is at or lessthan a threshold and when a determined torque loss from spark retard isnot less than a torque loss from turbo lag and the second conditionincludes when the torque demand is greater than the threshold and thedetermined torque loss from spark retard is less than the torque lossfrom turbo lag.
 16. The method of claim 11, further comprising, during athird condition, when a boost pressure is greater than the pressure ofthe intake manifold during driving intake airflow through the secondflow passage, opening the first throttle to direct intake airflowthrough the first flow passage, stopping driving the electriccompressor, and closing the compressor recirculation valve.
 17. Anengine method, comprising: directing intake airflow through a flowpassage including a turbine-driven compressor followed by a charge aircooler with a compressor recirculation valve opened, where thecompressor recirculation valve is configured to divert intake air aroundthe turbine-driven compressor; while compressing air cooled by thecharge air cooler by an electrically-driven compressor and directing itto an intake manifold.
 18. The engine method of claim 17, wherein thedirecting is in response to a driver tip-in, and where the compressingby the electrically-driven compressor is reduced while closing thecompressor recirculation valve after the turbine-driven compressor isspun up to a threshold level.
 19. The engine method of claim 17, whereinthe air compressed by the electrically-driven compressor is delivered tothe intake manifold while bypassing a throttle in a parallel passage.20. The engine method of claim 17, wherein an exhaust gas recirculationvalve is fully closed while directing intake airflow through the flowpassage and compressing air cooled by the charge air cooler and furthercomprising adjusting spark timing during compressor air cooled by thecharge air cooler by the electrically-driven compressor.